CN104081077A - Clutch arrangement - Google Patents

Abstract

The invention relates to a clutch arrangement (100), for example for a drive train of a vehicle, which comprises, according to one embodiment, a first component (280) that is disc-shaped in at least some sections and has a first frictional surface (230) on the disc-shaped section, a second component (290) that is disc-shaped in at least some sections and comprises a second frictional surface (240) on the disc-shaped section, said first and second frictional surfaces (230, 240) being designed and arranged to be able to be brought into a frictional engagement with one another and to be in contact with a liquid medium during operation, as well as a conveyor component (340) that comprises a conveyor surface (330) for said liquid medium and that is coupled to a drive component (150) in a substantially non-rotatable manner such that said conveyor surface (330); causes a flow of the liquid medium upon a rotation relative to said liquid medium. The conveyor component (340) engages, by means of the conveyor surface (330), with the first component (280) such that when said conveyor component (340) rotates, the first component (280) is made to rotate.

Description

Clutch pack

Technical field

Embodiments of the invention relate to the clutch pack in a kind of power assembly system that for example can be used in vehicle, for example Motor Vehicle.

Background technique

Clutch is applied to vehicular field, particularly automotive field with multiple different form.Clutch is here conventionally used in the vehicle frame of vehicle engine assembly system and carrys out transmitting torque, wherein clutch be for example arranged on drive unit, for example motor and with its follow-up speed changer being connected between.Can realize the separation of power assembly system thus, for example, also can under vehicle stop state, motor be remained in operation.The engine output shaft that clutch can rotate is in this case separated with static transmission input shaft.

Clutch also can be arranged in the power assembly system of vehicle in other cases.So for example in the situation that of combination drive, also can make if desired clutch be arranged between two different drive units or for making different drive units alternately separate and connect with transmission input shaft.Clutch in this case can with different drive unit technology, for example internal-combustion engine and motor and and the various drive technology use that combines.Clutch for example can with synchronize and asynchronous speed changer is combined with.Relevant speed changer can be manual transmission or automatic transmission, wherein can introduce by electric, electronics or other control impuls or hand shift if desired.

Clutch is contact based on set up frictional fit connection between corresponding part conventionally to this, and the driver part of these parts and relevant clutch and driven member connect.Just in case may occur while for example starting in the situation of very different rotating speeds, to this Conversion of Energy in the region of relevant rubbing surface, be heat, this heat can cause the undesirable heating of relevant rubbing surface and corresponding part.So for example use the clutch at enclosure interior circulation oil, this oil is drained the heat producing on rubbing surface from rubbing surface.

DE 10 2,009 016 414 A1 relate to a kind of clutch pack, wherein in the housing of clutch pack, form corresponding oil stream.DE 101 25628 A1 also relate to a kind of clutch pack, wherein construct like this at least one and are used to form the friction mechanism that frictional fit connects, so that oil carries out circulation, wherein by friction mechanism, carry out moment of torsion transmission.

In order to improve flowing of this fluid, as described in EP 1 813 831 A1, for example can use distribution device of cooling medium.This distribution device of cooling medium has connecting plate or the inclined-plane that can make with different geometries.Yet just in time spatially in narrow and small situation, be difficult to implement corresponding distribution device of cooling medium.

Therefore need in clutch pack, improve the rapport between the mobile and structure space demand of setting up liquid medium.

Summary of the invention

Clutch pack according to claim 1 meets above-mentioned requirements.

According to an embodiment for example for the clutch pack of vehicle engine assembly system comprise at least local be the first component of disc-shaped and at least part be the second component of disc-shaped, this first component has the first rubbing surface on the section of disc-shaped, this second component has the second rubbing surface on the section of disc-shaped, and wherein the first and second rubbing surfaces are constructed and are arranged to mutually to form friction engagement and contact with liquid medium in the running.Clutch pack also comprises transfer unit, and this transfer unit comprises the conveyor surface for liquid medium, and this transfer unit and driver part can not connect substantially with the relative rotation, makes conveyor surface when rotating with respect to liquid medium, make liquid medium flow.Transfer unit is meshed with first component by conveyor surface, and first component when transfer unit rotates is rotated.

The embodiment of clutch pack based on principle be, in order to form the transfer unit uses that flows, also for moment of torsion, transmit by making, can improve make liquid medium mobile and this required structure space is required between rapport.In order to realize this object, transfer unit is directly meshed with first component by conveyor surface, therefore the rotation by transfer unit also makes first component be rotated.Thus can be by identical parts, even by identical conveyor surface, liquid medium is flowed, this identical conveyor surface is also for driving first component and thus for transmitting torque.Therefore can be by larger the flowing that liquid medium is provided in the situation that structure space demand remains unchanged according to an embodiment's clutch pack, in the situation that mobile the remaining unchanged of liquid medium reduced structure space demand or realizes and coordinating between two targets, wherein not only increase flowing of liquid medium, also reduce structure space demand.

According in an embodiment's clutch pack, transfer unit is only meshed with first component by conveyor surface substantially at this.Whereby, because for example can save extra driving structure or driven structure, so can further improve above-mentioned rapport where necessary.

According in an embodiment's clutch pack, first component can be for example friction plate, for example inner attrition piece or outside friction disc, but can be also other the corresponding part for transmitting torque at slave end.

According in an embodiment's clutch pack, first component can be meshed with transfer unit by drive face, and making the surface of contact maximum between drive face and conveyor surface is 50% of conveyor surface area.Can make thus transfer unit be adjusted to flowing of high as far as possible or satisfactory liquid medium by least one conveyor surface.In other embodiment, surface of contact can be also the maximum 30%, 25%, 20%, 15% or maximum 10% of conveyor surface area.To this, can stipulate where necessary, the size of the minimum dimension of surface of contact is greater than the value of predetermining, with can be by moment of torsion from transfer unit by conveyor surface with drive face mechanically stable and be delivered to first component.Certainly this value can depend on the concrete structure of clutch pack.

According in an embodiment's clutch pack, conveyor surface can be continuous and smooth.Not only can simplify the manufacture of transfer unit thus, because can avoid if desired the complex geometric shapes of transfer unit, as a supplement or replace and can also realize in narrow and small structure space situation flowing of oriented liquid body medium targetedly.

According in an embodiment's clutch pack, conveyor surface can be approximately perpendicular to tangent direction, and this tangent direction is perpendicular to the spin axis of first component and perpendicular to vertically away from the radial direction of spin axis.Spin axis is exactly the spin axis in mathematical meaning, when transfer unit carries out corresponding sports, first component is around this spin axis rotation, and this spin axis is substantially consistent and also consistent with the spin axis of driver part in many examples with the spin axis of second component at this.Therefore spin axis is also referred to as the spin axis of clutch pack.

Because the conveyor surface of transfer unit is approximately perpendicular to tangent direction, thereby can reduce the axial load of first component and coupled other parts, because because corresponding conveyor surface is perpendicular to tangent direction thereby there is no that axial thrust load is passed.Correspondingly, the drive face of first component also can be approximately perpendicular to tangent direction.But also can advantageously affect flowing of the liquid medium that exists in clutch pack by directed conveyor surface correspondingly if desired.Thus, for example can be optionally and other part actings in conjunction of clutch pack, the corresponding orientation by conveyor surface makes liquid medium start roughly flowing of radially outward guiding from conveyor surface.

According to transfer unit in an embodiment's clutch pack, can there are a plurality of conveyor surfaces, these conveyor surfaces along the circle distribution of transfer unit arrange.Can bring up to thus power transmission and moment of torsion transmission on first component, because corresponding power is assigned to thus on more conveyor surface.

According in an embodiment's clutch pack, transfer unit can general arrangement be annular.Can simplify where necessary the manufacture of transfer unit thus.As the supplementary or replacement to this, also can correspondingly reduce the structure space of transfer unit.

Can single type structure transfer unit in this clutch pack.Alternatively, transfer unit also can comprise the transfer unit arcuate section of a plurality of ring arcs, and wherein single type is constructed the transfer unit arcuate section of each ring arc.Transfer unit arcuate section in a plurality of transfer unit bow-shaped parts can be roughly the same at this, but also can mutually differently implement.By single type, construct transfer unit and can avoid complicated manufacture method, wherein must interconnect by setting up the connection of form fit, material cooperation and/or power transmission cooperation a plurality of parts of transfer unit if desired.This is equally applicable to transfer unit arcuate section, and wherein these transfer unit arcuate sections can be simplified assembling and/or the manufacture of transfer unit in clutch pack framework.Yet in contrast to this, thus the design of the single type of transfer unit also can be simplified due to number of components still less and/or lower manufacture workload the whole manufacturing process of clutch pack.The part of single type structure refers at this part of just being made by a continuous blank.Therefore term " single type " is and term " integrated " or " single-piece " can synonymously be used.

To this, the connection that the static friction by relevant connection auxiliary equipment realized connection that power transmission coordinates, realized connection that material coordinates and the geometrical shape by relevant connection auxiliary equipment by the molecule of relevant connection auxiliary equipment or the interaction of atom and molecular force or atomic force has realized the connection of form fit.Therefore static friction requires particularly between two connection auxiliary equipments, to have normal component of force.

According in an embodiment's this clutch pack, distortion that can be by sheet-like workpiece, by the manufacture method of cutting or foundry engieering, manufacture the transfer unit arcuate section of transfer unit or ring arc.Thus, in the situation that the distortion by sheet-like workpiece manufacture transfer unit or transfer unit arcuate section can user cost favourable and simple, but many applications are there is to the manufacturing process of corresponding stability.Yet, in for example requiring high application, can use if desired the manufacturing process of more complicated, the manufacturing process of cutting or foundry engieering is manufactured transfer unit or transfer unit arcuate section.

According in an embodiment's clutch pack, driver part can be the housing that available liquid medium is filled or filled.Transfer unit can pass through the connection of form fit substantially and be connected with housing, so that transfer unit and driver part form, substantially can not counterrotatingly connect.Can make thus corresponding clutch pack be converted to special compact structure form, wherein directly use the housing of clutch pack as driver part.

According in an embodiment's this clutch pack, transfer unit can not be connected with housing with the relative rotation by riveting and/or socket connection.Can make thus transfer unit and housing form relative simple but mechanically stable, form fit and can not counterrotatingly connect.Thus can enough structures relatively simple instrument realize from housing to transfer unit compared with necessity transmission of high pulling torque and this moment of torsion is continued to pass to first component.

According to an embodiment's clutch pack, can also there is clamping element, in this clutch pack, driver part is the housing that available liquid medium is filled or filled, and this clamping element constructs and be provided for made the first and second rubbing surfaces mutually form friction engagement and/or departed from friction engagement by operation.Transfer unit can for example can not be connected with clamping element by riveting and/or socket connection with the relative rotation to this, and its middle shell for example can not be connected with connected element with the relative rotation by riveting and/or socket connection.Connected element can also for example can not be connected with transfer unit by riveting and/or socket connection substantially with the relative rotation.According in an embodiment's this clutch pack, transfer unit can directly be connected with clamping element, and transfer unit is connected with the housing as driver part by connected element.When rotating, housing force clamping element to rotate by connected element and transfer unit thus.Correspondingly, when the corresponding deceleration of driver part, clamping element is braked thereupon.Therefore under the specific operational situation of clutch pack, reduce under the given travel situation of corresponding vehicle or suppress clamping element and rotate freely.Can reduce if desired thus or even avoid clutch pack surprisingly to make a noise.

According in an embodiment's this clutch pack, connected element has a plurality of leaf spring element, these leaf spring element are for example connected by riveting and/or socket connection form fit ground with transfer unit, to form and substantially can not counterrotatingly to connect between transfer unit and connected element.Thus, the application of corresponding leaf spring element can realize substantially and can not counterrotatingly connect, but makes clamping element simultaneously and then transfer unit is moved along spin axis, and this spin axis is also referred to as axially.Because moment of torsion and/or connected element by generating may occur the distortion of leaf spring element along the axial displacement of spin axis, therefore set up at least one and substantially can not counterrotatingly connect.But for example due to aforementioned effect, relative to each other may there is slight torsion in the part of corresponding connection.In addition, use leaf spring element can realize more simply manufacturing of connected element and/or possible lighter aspect weight.

According in an embodiment's clutch pack, driver part is housing, and first component can comprise the disc-shaped parts with central recess, and wherein rubbing surface is arranged on the main surface that is approximately perpendicular to spin axis orientation of disc-shaped parts.At this, on a side stretching into the section in central recess of disc-shaped parts, mesh with transfer unit, wherein second component comprises another disc-shaped parts with central recess, wherein another disc-shaped parts are meshed with support in its outer radius.Therefore, first component can be inner attrition piece, and second component can be outside friction disc.Second component has another drive face on the side of the section away from central recess of another disc-shaped parts like this, and second component is meshed with support by this drive face.Correspondingly, support can have corresponding drive face equally.This clutch pack has been realized very compact structure form.

According to an embodiment's this clutch pack, can also there is clamping element, this clamping element constructs and is provided for made the first and second rubbing surfaces mutually form friction engagement and/or departed from friction engagement by operation, wherein clamping element limits first cavity volume of filling with liquid medium at least in part, and the cross-section area maximum having in the transversal plane that this first cavity volume extends therein at spin axis is equivalent to 20 times of the cross-section area of conveyor surface in this transversal plane.Therefore according in an embodiment's this clutch pack, when the first cavity volume rotation, this conveyor surface moves with significant degree and in the first cavity volume, causes that thus the above-mentioned of liquid medium flow.In the first cavity volume, by conveyor surface, provide the significant of liquid medium to flow thus, this cooling and thermal conductance for example flowing for rubbing surface goes out.In other embodiment, the cross-section area of the first cavity volume in transversal plane also can be equivalent to 15 times of the maximums, maximum 7.5 times, maximum 5 times, maximum 3 times or maximum 2 times of conveyor surface.

According in an embodiment's this clutch pack, clamping element can have the port hole that enters the first cavity volume for liquid medium, and this port hole is radially arranged near the At The Height or spin axis of conveyor surface.To this liquid medium under the operating condition in friction engagement, can flow through first and/or second component and support, therefore when conveyor surface rotate with respect to liquid medium, conveyor surface makes the mobile radially outward of liquid medium pass through the first and/or second rubbing surface of conveyor surface or along the first and/or second rubbing surface.Also can by housing, the first and second parts and clamping element, limit the first cavity volume substantially in such an embodiment.Certainly connected element or other corresponding part also can further limit the first cavity volume.It particularly relates to Sealing.

Liquid medium can be any being applicable to the liquid of the heat derivation producing on rubbing surface under the state of trackslipping in principle.Thus, for example liquid medium can be the oil that the external fluid feeding mechanism by clutch pack provides.

According to an embodiment's clutch pack, can be for example single plate clutch, two-plate clutch or general said multiple-disk clutch.This clutch can be for example and the starting clutch of asynchronous speed changer (for example automatic transmission) combination or the cut-off clutch combining with synchrom esh transmission.

Accompanying drawing explanation

Below with reference to accompanying drawing, describe and set forth a plurality of embodiments in detail.

Fig. 1 shows according to the transverse sectional view of an embodiment's clutch pack;

Fig. 2 shows the stereogram of the transfer unit of clutch pack in Fig. 1;

Fig. 3 shows according to the stereogram of the transfer unit arcuate section of an embodiment's clutch pack;

Fig. 4 shows according to the transverse sectional view of another clutch pack of another embodiment;

Fig. 5 shows the stereogram of the feasible transfer unit of clutch pack in Fig. 4;

Fig. 6 shows according to the stereogram of the transfer unit arcuate section of an embodiment's clutch pack;

Fig. 7 shows according to the transverse sectional view of another clutch pack of an embodiment;

Fig. 8 shows according to the transverse sectional view of another clutch pack of an embodiment;

Fig. 9 shows according to the transverse sectional view of another clutch pack of an embodiment.

During the accompanying drawing that embodiment of the present invention is shown is below described, identical reference character represents identical or similar part.In addition, in an embodiment or accompanying drawing, repeatedly occur that still common part and the object of describing one or more features used recapitulative reference character.Only otherwise can in describing, clearly or impliedly draw other implications, having so part identical or recapitulative reference character or object can be embodied as identical or also may be embodied as if desired different in the size of single, a plurality of or all characteristic aspect, for example part or object.

Reference numerals list

100 clutch packs

110 housings

120 first clamshells

130 second clamshells

140 are welded to connect

150 driver parts

160 welding screws

170 internal surfaces

180 friction packs

190 driven members

200 bottom wheel hubs

210 internal tooth portions

220 internal surfaces

230 first rubbing surfaces

240 second rubbing surfaces

250 outside friction discs

260 friction covering faces

270 inner attrition pieces

280 first components

290 second components

300 spin axiss

305 port holes

310 sections

320 drive faces

330 conveyor surfaces

340 transfer units

350 rivetings

360 Sealings

370 sections

380 another drive faces

390 supports

400 rivetings

410 first wheel flanges

420 vibration dampers

430 first elastic elements

440 helical springs

450 first cover plates

460 second cover plates

470 slotted holes

480 another rivetings

490 spacing washers

500 spacing washers

510 slotted holes

520 second hub flange

530 second elastic elements

540 helical springs

550 bearings

560 sections

565 another bearings

570 dividing plates

580 anterior wheel hubs

590 piston pressure chambeies

600 piston areas

610 pistons

620 clamping elements

630 Sealings

640 Sealings

650 input holes

660 sealing surfaces

670 sealing surfaces

680 first seal faces

690 lug bosses

700 second seal faces

710 sections

720 first cavity volumes

730 part cavity volumes

740 second cavity volumes

750 surface segment

The 760 piston back sides

770 primary sealing areas

780 secondary sealing areas

790 transition zones

800 transfer passages

810 supply units

820 inflow regions

830 flow out region

840 pump impeller hubs

850 Sealings

860 holes

870 welding

880 welding

890 weight balancing parts

900 space washers

910 planar section

920 welding

930 recesses

940 teeth

950 sections

960 outer cover

970 holes

980 transfer unit arcuate sections

990 rivetings

1000 other rivetings

1010 leaf spring element

1015 connected elements

1020 cup springs

1030 cavity volumes

1040 cup springs that recline

1050 convex shoulders

1060 flanged structures

1070 compress point

1080 transmission input shafts

1090 outer toothed portion

1100 have the groove of Sealing

1110 flow channels

1120 attachment holes

Embodiment

Fig. 1 shows according to the transverse sectional view of an embodiment's clutch pack 100.Clutch pack 100 for example can be used in the framework of vehicle engine assembly system at this, thereby for example the moment of torsion being provided by drive unit can be passed to speed changer or miscellaneous part dividually.Therefore clutch pack 100 for example can be with synchrom esh transmission combination in the situation that as cut-off clutch or for example, with asynchronous speed changer, when corresponding automatic transmission case interacts as starting clutch.

Thus, clutch pack 100 comprises housing 110, and this housing is embodied as the double-piece type housing with the first clamshell 120 and the second clamshell 130 in the present invention, and wherein the second clamshell 130 also represents the outer cover that starts pusher side of clutch pack 100.Two clamshells 120,130 interconnect by being welded to connect 140 at this.Therefore housing 110 can be filled or filling liquid medium, and this liquid medium is for example applicable to absorbing and what derive the housing 110 inner heats that produce is oily or other liquid.

In the clutch pack 100 shown in Fig. 1, the second clamshell 130 as driver part 150 and thus housing 110 as driver part 150.For this purpose, the second clamshell 130 has for being fixed on the welding screw 160 on the twisted plate of drive unit, for example motor or flywheel or on other parts of power assembly system.Also can adopt alternatively pin or other fixed structure to replace welding screw 160 to fix clutch pack 100.

More precisely, the clutch pack shown in Fig. 1 100 is multiple-disk clutch or multidisc clutch.Clutch pack 100 correspondingly has friction packs 180 in the inner chamber of housing 110, this friction packs has a plurality of the first rubbing surfaces 230 and a plurality of the second rubbing surface 240, wherein, the first rubbing surface by the assembly that the following describes at least substantially can not be with the relative rotation with the driver part 150 of clutch pack and housing 110 connects and the second rubbing surface 240 can not connect with the driven member 190 of clutch pack at least substantially with the relative rotation.More precisely, driven member 190 is bottom wheel hubs 200, and this wheel hub can connect by internal tooth portion 210 and the unshowned transmission input shaft form fit of Fig. 1 ground.Transmission input shaft has the outer toothed portion of corresponding internal tooth portion 210.

In embodiment shown in Fig. 1, clutch pack 100, friction packs 180 comprises the first rubbing surface 230-1 on the internal surface 220 that is configured in housing 110 or the second clamshell 130, and corresponding the second rubbing surface 240-1 of this first rubbing surface and outside friction disc 250-1 is in friction engagement or can form friction engagement.Outside friction disc 250 is used friction covering face 260-1 coating at this, and the second rubbing surface 240-1 is configured on this friction covering face.In contrast to this, in the situation that housing 110 is formed from steel equally, the first rubbing surface 230-1 is directly configured on the internal surface 220 of housing 110,, for example, is shaped to steel surface that is.

Outside friction disc 250-1 has another friction covering face 260-2 in the side away from internal surface 220, and this friction covering face forms another second rubbing surface 240-2 on a surface.The second rubbing surface 240-2 and inner attrition piece 270-1 are in friction engagement or can form friction engagement by corresponding the first rubbing surface 230-2 and this inner attrition piece 270-1.

Friction packs 180 also has another outside friction disc 250-2 and another inner attrition piece 270-2, wherein, outside friction disc 250-2 has corresponding a plurality of friction covering face 260 equally, but for the sake of clarity, in Fig. 1, equally only there are several friction covering faces to use reference character to represent, for example corresponding the first and second rubbing surfaces 230,240 that provide.Outside friction disc 250-2 is arranged between two inner attrition piece 270-1 and 270-2 at this.Therefore friction packs 180 is limited by inner attrition piece 270-2 in a side of the internal surface 220 away from housing 110.

Inner attrition piece 270 is embodied as disk-shaped substantially steel part and represents that corresponding at least local disk-shaped first component 280, the first rubbing surfaces 230 are arranged in the region of the dish type section on this first component at this.Outside friction disc 250 is also embodied as at least local disk-shaped second component 290 by its friction covering face 260, and this second component has the second rubbing surface 240 on its dish type section.Certainly, in other embodiment, also friction covering face 260 can be set on each miscellaneous part.

Inner attrition piece 270 and outside friction disc 250 all have respectively a central recess with respect to spin axis 300, and wherein, inner attrition piece 270 and outside friction disc 250 just can arrange rotatably around spin axis 300.Therefore, spin axis 300 also represents the spin axis of clutch pack 100 and is also expressed as axial direction in mathematical meaning.

For moment of torsion being delivered to inner attrition piece 270 from the housing 110 as driver part 150, this inner attrition piece has respectively section 310-1,310-2, on a side on these sections, be configured with respectively one and drive face 320-1,320-2, inner attrition piece 270 keeps engagement with the conveyor surface 330 of transfer unit 340 respectively like this by these drive faces, that is, when transfer unit 340 rotation, each inner attrition piece 270 (first component 280) also starts to be rotated.Transfer unit 340 is that annular and the circumference around spin axis 300 along clutch pack 100 extend in this general arrangement.Transfer unit 340 in the embodiment shown in fig. 1 general arrangement is bellows-shaped, the tangent direction that circumferentially, is approximately perpendicular to that makes conveyor surface 330 be basically perpendicular to clutch pack 100 stretches, and wherein this tangent direction is vertically arranged on spin axis 300 and is vertically located at corresponding cutting plane away from spin axis 300 in the radial direction.

More precisely, transfer unit 340 has a plurality of conveyor surfaces 330 at this.These conveyor surfaces circumferentially for example arrange equably along transfer unit 340.The section 310 of inner attrition piece 270 correspondingly has the drive face 320 of respective numbers, and a plurality of conveyor surfaces 330 and these drive faces are meshed.The section 310 of transfer unit 340 and inner attrition piece 270 forms a plurality of intermeshing tooth portion thus.Can make thus torque distribution to be passed on more conveyor surface 330 and drive face 320, can make if desired thus corresponding higher moment of torsion be delivered on inner attrition piece 270 and therefore by transmitting according to the clutch pack 100 shown in an embodiment.

But before being shown specifically and setting forth combination Fig. 2 of corresponding transfer unit 340 and the embodiment of Fig. 3, first according to an embodiment, continue to describe clutch pack 100.

Transfer unit 340 by riveting 350, can not relatively rotate with Sealing 360 and the second clamshell 130 and form fit connect.Thus, by riveting 350 and if desired by Sealing 360 by driver part 150, be that rotatablely moving of housing 110 is delivered on transfer unit 340 and is delivered to thus on conveyor surface 330.By conveyor surface 330 and drive face 320, inner attrition piece 270 and transfer unit 340 are meshed, transfer torque to thus on inner attrition piece 270.

Outside friction disc 250 (second component 290) also has section 370-1 and 370-2, and these sections are meshed and absorb and be delivered to the moment of torsion outside friction disc 250 from inner attrition piece 270 in the situation that having set up frictional connection with the support 390 also referred to as outside friction disc support by corresponding other drive faces 380.

Support 390 has the structure that is roughly pot shape that comprises central recess, and this support connects with the first wheel flange 410 of two-stage shock absorber 420 by riveting 400.First wheel flange 410 connects with support 390 by separator or spacing washer 500 at this.Spacing washer 500 is configured to a part for riveting 400 at this, yet also can separately implement with riveting.

Vibration damper 420 has a plurality of the first elastic elements 430, and these elastic elements are along the circumference setting of first wheel flange 410 and with one end and first wheel flange, lean respectively.The first elastic element 430 is embodied as helical spring 440 at this.Helical spring 440 or the first elastic element 430 lean by other one end and the first cover plate 450 respectively, this first cover plate according to the structure shown in Fig. 1 also referred to as right cover plate.The first cover plate 450 is connected with the second cover plate 460 by separator or spacing washer 490 at this, and this second cover plate is also referred to as left cover.Left cover forms the not closed housing of damping means 430 together with right cover plate.The second cover plate 460 this single type lead to inner radial.

Riveting 400 and spacing washer 500 be slotted hole 470 through ring arc at this, support 390 is connected by the first wheel flange 410 of riveting and vibration damper 420, and this slotted hole defines two cover plates 450,460 to the maximum range of motion of first wheel flange 410 and relevant support 390.

Compare towards the extension of the direction of spin axis 300 with the first cover plate 450, the second cover plate 460 obviously extend in the radial direction farther.Therefore, the first cover plate 450 can not be connected by relative machinery with the second cover plate 460 with spacing washer 490 rotatably by another riveting 480.Spacing washer 490 extends through at this slotted hole 510 that is similarly ring arc in the second hub flange 520.The second hub flange 520 and the first cover plate 450 are coupled to each other by the second elastic element 530 at this, and this second elastic element is embodied as again helical spring 540 at this.The second cover plate 460 inner radial through having the second elastic element 530 the second cluster spring single type pass.

The elastic element that certainly, also can adopt other in other embodiments of clutch pack 100 is as the first and second elastic elements 430,530.Therefore, for example, can use tubular spring, but as long as technical specifications, particularly leading chemistry and/or the boundary conditions of calorifics can correspondingly be met in housing 110, so also can use based on elastomeric elastic element.

The second hub flange 520 also by can not counterrotating link with bottom wheel hub 200, be that driven member 190 is connected.At this, for example also can use riveting.But also can use other interconnection techniques that for example form fit, power transmission cooperation and/or material coordinate.Therefore together with for example the second hub flange 520 can being welded to each other with bottom wheel hub 200.But for example also can be used as, supplement or plug link alternatively.Thus, replacing other aforesaid rivetings also to can be used as supplements or alternatively makes these rivetings be embodied as plug-in connector or realize by other interconnection techniques.

Moment of torsion is delivered to cover plate 450,460 via elastic element 430 by support 390 and first wheel flange 410 from outside friction disc 250 thus, when the first and second rubbing surfaces 230,240 are when intermeshing, this moment of torsion continues pass to Fig. 1 unshowned transmission input shaft via the second elastic element 530 by the second hub flange 520, bottom wheel hub 200 from described cover plate.

In embodiment shown in Fig. 1, the second hub flange 520 by bearing 550, more precisely in the present invention by axial sliding bearing, with the first clamshell 120 relatively, can be supported rotatably with respect to spin axis 300.The second hub flange is at a stay section 560 of portion's wheel hub 200 of the side upper support away from bearing 550 of this second hub flange 520, and this section self can rotatably be supported around spin axis 300 with respect to dividing plate 570 by another bearing 565.Another bearing 565 is also axial sliding bearing in the embodiment shown in fig. 1.Dividing plate 570 is a part for anterior wheel hub 580 and at least one side of abuts piston pressure chamber 590.In axial direction, along sense of rotation 300, the piston area 600 by piston 610 defines this piston pressure chamber.Piston 610 represents clamping element 620 as shown in the following describes, and this clamping element constructs and be provided for to make the first and second rubbing surfaces 230,240 mutually form friction engagement by operating.In other embodiment, clamping element 620 can be configured to separated friction engagement equally.Same as middle elaborating is described below, the clutch pack shown in Fig. 1 is normally disengaged clutch, wherein under stress-free state, do not have friction engagement or only have friction engagement on not half less than operate in the situation that.In embodiment shown here, clamping element 620 is configured to make the first and second rubbing surfaces 230,240 mutually form friction engagement by operating thus.

By two Sealings 630 and 640 on the one hand with respect to clamping element 620 and on the other hand with respect to anterior wheel hub 580 packed-piston pressure chambers 590.In order to fill the respective media under pressure state in piston pressure chamber, this medium is for example and the identical liquid medium of remaining part that can be used for filling housing 110, anterior wheel hub 580 has the input hole 650 to piston pressure chamber 590, this input hole is in the region near the second clamshell 130 of hydraulically operated connection piston pressure chamber 590 and central recess, and transmission input shaft is also arranged in this region.

In order to make clamping element 620 move along sense of rotation 300, two Sealings 630,640 are separately positioned in the corresponding recesses in dividing plate 570 and anterior wheel hub 580 and are oriented, and the corresponding sealing surface 660 and 670 extending along sense of rotation 300 of these two Sealings and clamping element 620 is contacted.

Clamping element 620 radially extends, and from spin axis 300, starts to extend until the At The Height of inner attrition piece 270 and outside friction disc 250 perpendicular to this spin axis.Clamping element 620 has the first seal face 680 in this region, and this first seal face is faced the first and second rubbing surfaces 230,240, is outside friction disc 250 and inner attrition piece 270.By penetrating of clamping element 620, form the first seal face 680 in the embodiment shown in fig. 1, by this first seal face, form lug boss 690, this lug boss is placed in this region towards the first and second rubbing surfaces 230,240 with respect to clamping element 620.Lug boss 690 is by for making, blank, for example steel or other metallic material of clamping element 620 is connected with clamping element and therefore have the elastic constants less than clamping element 620 thus.Clutch pack 100 shown in Fig. 1 has a plurality of lug bosses 690 at this, these lug bosses along the circle distribution of clutch pack arrange.At this, can arrange equably, also can arrange unevenly.

Lug boss 690 contacts with the back side of inner attrition piece 270-2 by the first seal face 680 at this.By lug boss 690 structure clamping elements 620, with the first seal face 680 by clamping element 620, provide the impacting force towards the first and second rubbing surface 230,240 directions thus, by this impacting force, can between two rubbing surfaces, set up friction engagement.Due to the elastic constants that the remaining part with respect to clamping element 620 reduces, can realize slight joint by the first seal face 680 is set on lug boss 690 if desired.

But clamping element 620 has the second seal face 700 in addition, this second seal face is not configured on lug boss 690 but is configured on the section 710 of clamping element 620.About the elastic performance of this section, i.e. its elastic constants aspect for example, section 710 is obviously different with other regions of clamping element 620, and for example lug boss 690 is exactly this situation.Therefore, the elastic constants of section 710 is typically obviously greater than the elastic constants of lug boss 690, for example at least 2 times, at least 5 times or at least 10 times.

If at this moment clamping element 620 moves towards the first and second rubbing surfaces 230,240 along spin axis 300, in Fig. 1 to left movement, so first the first seal face 680 by lug boss 690 carries out relatively slight joint.If clamping element 620 continues motion, the distortion of lug boss 690 increases and is applied to by the first seal face 680 impacting force that increases on friction plate 250,270 and then be applied on corresponding rubbing surface 230,240 and increases so.If the degree of at this moment clamping element 620 motions makes this clamping element cause impacting force by the second seal face 700 of section 710, the impacting force that obviously higher almost jump type may be increased is so delivered on rubbing surface 230,240.From the distortion of the resiliently deformable of clamping element 620 and the friction covering face 260 that may occur, can find out the end-state that at this moment clamping element 620 connects completely in clutch pack 100.Certainly, in this region, also still can the power towards the direction driving of the first and second rubbing surfaces 230,240 continue to be improved by corresponding raising clamping element 620, but not need clamping element 620 to move significantly.

Aforesaid from the transition of the first seal face 680 to second seal faces 700; although the first seal face 680 conventionally goes back and inner attrition piece 270-2 contacts; but compare with the second seal face 700, transmit obviously less power, this power is drawn by the relation of the corresponding elastic constants of lug boss 690 and the elastic constants of section 710.Clamping element 620 is roughly resisted against on inner attrition piece 270-2 along its whole circumference under this state.

In order to avoid effectively compressing the movement of point when connecting clutch pack 100, can be considering corresponding counterpart in the structure of the clamping element 620 shown in Fig. 1, make consider in this case inner attrition piece 270-2 in the situation that the surperficial mid point of two seal faces 680,700 of being correlated with or effectively point of contact roughly overlap.In addition, in embodiment shown in Fig. 1, clamping element 620, can increase seal face.Thus, due to larger area, can transmit larger impacting force if desired, and substantially not need worry can change effective compression point.

If desired, the displacement that effectively compresses point may cause the change of pressure dependence leading on the first and second rubbing surfaces 230,240, for example, can cause this change by the elasticity of friction covering face 260 and relevant inner attrition piece 270, the elasticity of outside friction disc 250 and the elasticity of miscellaneous part.Thus, where necessary can mobile rubbing surface 230,240 on such point, that is, the maximum heat that the friction occurring owing to connecting produces can be passed on this aspect.Therefore may cause in some cases the reduction to the cooling effect of the first and second rubbing surfaces 230,240 of liquid medium in aforesaid, housing 110 inside.Also can cause the inhomogeneous use of friction covering face 260.Because inner attrition piece 270 and outside friction disc 250 can be in axial motions, thereby also may cause friction plate 250,270 its each tooth portion region or with the mesh regional of transfer unit 340 and support 390 in occur slight crookedly, may further strengthen corresponding effect thus.

Clamping element 620 and outside friction disc 250, inner attrition piece 270 and Sealing 360 surround the first cavity volume 720 of the inner volume of clutch pack 100 at least partly at this.As above about the brief narration of transfer unit 340, transfer unit 340 has a plurality of conveyor surfaces 330, these conveyor surfaces are not only meshed with the drive face 320 of inner attrition piece 270, and these conveyor surfaces 330 are configured to realize flowing of liquid medium equally when conveyor surface moves with respect to the liquid medium in housing 110 inside.For this reason, transfer unit 340 can not be connected with the relative rotation with the housing 120 as driver part 150.Conveyor surface 330 is especially arranged in the first cavity volume 720 in the embodiment shown in fig. 1, therefore at conveyor surface 330, when liquid medium moves, carries the liquid medium in the first cavity volume 720.

For conveying liquid body medium as far as possible effectively, related to this can be advantageously, inner attrition piece 270 is meshed with the conveyor surface 330 of transfer unit 340 by drive face 320, and making the surface of contact maximum between relevant drive face 320 and conveyor surface 330 is 50% of conveyor surface area.As long as enough power transmission and moment of torsion on the drive face 320 of guaranteeing to have enough stability and be delivered to inner attrition piece 280 by conveyor surface 330 transmit, so further reduce aforementioned proportion and can improve flow condition.Therefore it can be favourable in other embodiment, for example aforementioned proportion being limited in to maximum 30%, maximum 25%, maximum 20%, maximum 15% or maximum 10%.According to the dual functions of conveyor surface and Surface of action, try to achieve the lower limit of this ratio.

As shown in Figure 1, conveyor surface 330 is continuous and smooth at this.This conveyor surface along circumferentially or tangentially, be approximately perpendicular to spin axis 300 and from spin axis start in the radial direction away from this spin axis arrange.In this moment of torsion transmission characteristics that is configured in conveyor surface 330, can be favourable, because when being applied to axial force on inner attrition piece 270 (first component 280) by drive face 320 along spin axis 300 and can not being avoided completely, make thus this axial force be reduced.Yet this structure of conveyor surface 330 cause flowing medium, for example oil mobile aspect can be also favourable.Can cause where necessary so thus the flowing towards the liquid medium of the first and second rubbing surfaces 230,240 of radially outward substantially.

Relevant friction plate 270,250 and the friction covering face 260 that may be provided with thereof can be configured to, the liquid stream of liquid medium can flow through these friction plates and friction covering face.For this reason, corresponding friction plate 250,270 is connected with this friction plate or comprises that the part of this friction plate can have passage or fluid passage, and liquid medium can radially pass these passages.These passages for example may be embodied as lineal shape, but also may be embodied as crooked linear and extend in the region of rubbing surface 230,240.Can discharge thus near be spatially arranged in liquid medium the frictional energy just freely distributing in the region of rubbing surface 230,240 and heat and go out by leading liquid conductance.

In the transversal plane shown in Fig. 1, conveyor surface 330 has such cross-section area, and this cross-section area self comprises that the second cavity volume 720 is not very little cross-section area part in relevant cutting plane.In order to realize the large as far as possible relevant conveying effect of transfer unit 340, can be in the embodiment of clutch pack 100 with respect to the cross-section area of conveyor surface 330, select like this cross-section area of the first cavity volume 720, the cross-section area of the first cavity volume is equivalent to 20 times of the maximums, maximum 15 times, maximum 10 times or maximum 7.5 times of the cross-section area of conveyor surface 330.Even can in the embodiment of clutch pack, use also will be less coefficient.Thereby 5 times of the maximums of conveyor surface 330, maximum 3 times or maximum 2 times of cross-section areas as the first cavity volume 720 can be set.Certainly in other embodiment, also can there is the multiple larger than above-mentioned multiple.

In order to make liquid medium correspondingly flow to conveyor surface 330, clamping element 620 is in the radial direction at the height of conveyor surface 330 or have the unshowned port hole 305 of Fig. 1 near spin axis 300, and this port hole is also referred to as boring or through hole.This through hole is arranged on the radially outer of Sealing 360 at this, and passes in the first cavity volume 720.Liquid medium can enter the first cavity volume 720 through the unshowned through hole of Fig. 1 thus, and liquid medium is carried by rubbing surface 230,240 by conveyor surface 330 radially outwards that can rotate with respect to liquid medium in this first cavity volume.The there that is flowing in of liquid medium enters into the part cavity volume 730 of housing 110, and vibration damper 420 is also arranged in this part cavity volume.In part cavity volume 730, the heat being dispersed on liquid medium can be dispersed on miscellaneous part, for example housing 110.Part liquid medium can enter in the first cavity volume 720 again by the unshowned port hole 305 of Fig. 1, and another part liquid medium can leave part cavity volume 730 by bearing 550.At this dividing plate 570, part cavity volume 730 and piston pressure chamber 590 are separated.

The conveying effect of transfer unit 340 especially when thering is speed discrepancy between transfer unit 340 and liquid medium transfer unit limited and flowed.Transfer unit can not utilize the relative movement between driver part 150 and driven member 190 by counterrotating link by described.But at the first and second rubbing surfaces 230,240, be in contact with one another while having different rotating speeds, this relative movement is present in sliding area especially.In this case at the many heats of region generating of rubbing surface 230,240, these caloric requirements are derived by liquid medium just.If finally there is rotating speed balance, be that clutch pack 100 engages, so substantially do not produce new heat, make peace greatly housing 110 while rotating together thus at clutch pack, due to transfer unit 340 and liquid medium, having identical speed is not just problem to carrying the inhibition of effect.

Sealing 360 separates the second cavity volume 740 and the first cavity volume 720.At this, also limit at least partly the second cavity volume 740 in surface segment 750 and the piston back side 760 of the internal surface 220 by the second clamshell 130, wherein, the piston back side 760 is resisted against in the side away from piston area 600 of clamping element 620.

If because transfer unit 340 causes occurring pumping action with its conveyor surface 330 with respect to the relative movement of liquid medium, so because hydraulic effect makes (static state) pressure decreased in the first cavity volume 720.By Sealing 360, the first cavity volume 720 and the second cavity volume 740 are separated, the conveying effect that may occur regardless of transfer unit 340 thus how, in can making the second cavity volume in the second cavity volume 740, leading pressure roughly remains unchanged, the pressure difference that at least restriction may occur due to other effects.Thus in the relative movement due to transfer unit 340 or under caused pumping action, act on power on the piston back side 760 roughly not by carry effect and thus the motion by transfer unit 340 be affected.

In other words, can, by using Sealing 360 to make pressure maintenance leading in the second cavity volume 740 more constant, when operation clamping element 620, can substantially suppress thus, still at least reduce because the pressure during liquid is imported to piston pressure chamber 590 or in the second cavity volume occurring while taking away from piston pressure chamber changes and the variation of the power on the piston back side 760 thus.By making to keep being consistently applied to the corresponding power on the piston back side 760, can improve if desired by operation clamping element 620 restriction of connection situation, disengagement situation or specific slip condition on rubbing surface 230,240.If desired can be by using corresponding Sealing 360 to improve according to controllability and the operability of an embodiment's clutch pack 100.

According to the concrete structure of Sealing 360, can pass through to change the radial position of Sealing 360, thereby construct the second cavity volume 740 smaller or greaterly.Yet, in the actual size of this first cavity volume 720, being preferably less than position and/or the size of the surface segment of clamping element 620, this surface segment limits the second cavity volume 740 at least partly.Therefore when clutch pack 100 rotation, on the liquid medium in the second cavity volume 740 and piston pressure chamber 590, there is centrifugal force.This centrifugal force causes the formation of pressure, and this pressure starts to be applied to clamping element 620 and causes reverse power mutually from both sides.Therefore, the radial position of Sealing 360 and transition region 790 thereof exerts an influence to following aspect: whether because centrifugal action can change by pressure, cause that extra effective power is applied on clamping element 620, the size of this power and action direction how.

For example, if the transition region 790 of Sealing 360 is towards near the dislocation of spin axis 300, thereby the extension of the surface segment of clamping element 620 radially reduces and the second cavity volume 740 diminishes, from the side action of the second cavity volume 740, to the power clamping element 620, also diminish so.The pressure causing due to centrifugal force in piston pressure chamber 590 causes not having the effective masterpiece that vicissitudinous situation is larger to be used on clamping element 620 than the position of Sealing 360 thus.Therefore the centrifugal force occurring in piston pressure chamber 590 is undercompensation.

Correspondingly can realize and act on the overcompensation of the centrifugal pressure on clamping element 620 or roughly fully compensate this centrifugal pressure by the variation set position of transition zone 790.To this, the size of the pressure occurring in the second cavity volume 740 due to centrifugal force under correlation circumstance can be set for, this pressure can not be excessive can not be too small, thereby hinder engagement movement or the detaching motion that even stops clamping element 620.

In addition, as previously mentioned, Sealing 360 is not only configured at hydraulically operated separated the first cavity volume 720 and the second cavity volume 740, but also the power that is configured to make clamping element 620 get back on its initial position when not operating clamping element is applied on clamping element 620 or has on another parts of at least part of disk-shaped section.Sealing also can correspondingly apply this power, and clamping element 620 is got back on its initial position.In the initial position shown in Fig. 1, the degree that friction engagement is just unclamped or it at least fluffs between the first and second rubbing surfaces 230,240 makes not have obvious moment of torsion to transmit by clutch pack 100.To this, by introducing corresponding fluid chamber, by input hole 650 to piston pressure chamber 590, operate clamping element 620.

In order to realize the dual functions of Sealing 360, Sealing 360 has primary sealing area 770 and secondary sealing area 780, and these two sealing surfaces interconnect by transition zone 790.Primary sealing area 770 and secondary sealing area 780 are all approximately perpendicular to spin axis 300 and along this spin axis space at this.These two sealing surfaces 770,780 this radially, perpendicular to spin axis 300 also space, wherein in the Sealing 360 shown in Fig. 1, secondary sealing area 780 is arranged on the radially inner side of primary sealing area 770.Thus, transition zone 790 has outer surface of cone shape.Certainly, in other embodiment, two sealing surfaces 770,780 also can radially reversally arrange.

At this, two sealing surfaces 770,780 are resisted against in the corresponding plane or circular segments and clamping element 620 of housing 110 or the second clamshell 130.These two sealing surfaces can carry out if desired surface treatment, for example carry out turning, to form corresponding matched seal face according to concrete structure.

If the motion due to clamping element 620 causes Sealing 360 distortion now, so especially, transition zone 790 is also out of shape, wherein, even because first the plane structure of two sealing surfaces 770,780 is that plane coating is preferential according to trend under Sealing distortion or its geometric orientation with respect to clamping element 620 and the second clamshell 130 change situation.Yet, according to the deformation extent of Sealing 620, also can cause in two sealing surfaces 770,780 at least a portion of one to lift or roll.But in this case can be at least partly but also can fully make if desired related seals face 770,780 only contact corresponding part to wire, be clamping element 620 or the second clamshell.But conventionally always there is at least one linear contact area.Thus, even also can make Sealing 360 maintain at least partly sealing effect in the situation that of clamping element 620 motion.In order to improve Sealing 360 fixing on the second clamshell 130, also to make Sealing in the side away from transition zone 790, there is the section that the shape with the second clamshell 130 matches, with in the radial direction with axial direction on, along the direction of spin axis 300, form at least partly the connection of form fit.The connection of this form fit if desired also can be only as the assembling assistant tool of Sealing 360 or the assistant tool of feeling relieved.Section also referred to as wheel rim or edge can be set as a supplement or alternatively for mechanically stable Sealing 360.Can reduce where necessary or prevent that Sealing 360 is along circumferential distortion when clamping element 620 is advanced along spin axis 300 completely by this section thus.Therefore, for example can be along circumferential formation ripple when load correspondingly.Also can cancel if desired the above-mentioned form fit about Sealing 360 and the second clamshell 130.

Therefore, in embodiment shown in Fig. 1, clutch pack 100, Sealing 360 is of use not only in separated the first and second cavity volumes 720,740 on fluid technique, but also realized extra function, before operation clamping element, make clamping element 620 turn back to initial position, thereby clutch pack 100 is normally disengaged clutch assembly just.If desired also can be by being for example other corresponding elastic element secondary seals 620 of complementary cup spring, diaphragm spring, leaf spring or helical spring form.

Certainly, in other embodiment, Sealing 360 also can be applied to this power on clamping element 620 or another parts, thus, clutch pack 100 is expressed as normal-close clutch device assembly, does not need to operate in the friction engagement between the first and second rubbing surfaces 230,240 in this clutch pack.In other words, also referred to as the Sealing 360 of the diaphragm seal prestressing force that not only can be under pressure as shown in Figure 1, and can under tension prestressing force.Thus, for example can realize normal-close clutch device assembly.

Clutch pack 100 shown in Fig. 1 is three pipeline types, and wherein input hole 650 represents three pipelines or passage, by these pipelines or passage, can, for piston pressure chamber 590 supply liquid mediums, also supply if desired other liquid medium.For clamping element 620 can be moved, the second cavity volume 740 is connected on fluid technique by the transfer passage 800 being shown in dotted line in Fig. 1, and this transfer passage is guided in the supply unit 810 that passes to the second cavity volume 740.Transfer passage 800 passes to inflow region 820 at this, along the unshowned transmission input shaft of Fig. 1, guides this inflow region.Transfer passage 800 and supply unit 810 can be realized inflow and the outflow of liquid medium thus in the situation that of clamping element 620 motion.Therefore, this transfer passage and supply unit are for the compensation of corresponding cavity volume.

Inflow region 820 at this by the internal tooth portion 210 at transmission input shaft and some teeth that lack in corresponding outer toothed portion and liquid medium, be that the entrance of oil or transmission oil is connected.Conventionally, in the internal tooth portion 210 of the unshowned transmission input shaft of Fig. 1 and the region of corresponding outer toothed portion, save on a tooth or a plurality of positions on the circumference along respective teeth portion and save two or more adjacent teeth, on these positions, form oil thus and run through pipeline, these oil run through pipeline is connected inflow region and speed changer on fluid technique.More precisely, on three positions, lack respectively in the embodiment shown in fig. 1 two adjacent teeth in associated teeth portion, to form oil, run through pipeline.

By inflow region 820, be not only the second cavity volume 740 supply liquid mediums, and by inflow region 820 be integrated in the oily guide duct attachment portion cavity volume 730 on fluid technique in bearing 565.In other words, pass the oily guide channel guiding oil input of corresponding outer toothed portion, inflow region 820 and the bearing 565 of internal tooth portion 210 and transmission input shaft.At this, the input hole 650 that leads to piston pressure chamber 590 is separated with inflow region 820 by the same unshowned sealed department of Fig. 1.Inflow region 820 is therefore as second pipe.

Liquid medium can leave part cavity volume 730 by bearing 550 and the corresponding oily guiding device or the oily guide channel that flow out in region 830.Flowing out region 830 is configured between bottom wheel hub 200 and pump impeller hub 840 and has ringwise cross section substantially at this.Pump impeller hub 840 is sealed with respect to bottom wheel hub 200 by Sealing 850 at this.Can take away and enter the liquid medium flowing out in region 830 by the hole 860 also referred to as discharge equipment.At clutch pack 100 mesopores 860 shown in Fig. 1, at this, be connected with speed changer oil sump or other oil vessels or liquid medium container.Therefore hole 860 forms the 3rd pipelines with outflow region 830.

The delivered volume that can be circulated in the inside of housing 110 by its conveyor surface 330 by transfer unit 340 surpasses under many circumstances by inflow region 820 and flows out that region 830 flows to the volume of housing 110 and many times of the volume of draining by it.Therefore, by the conveyor surface 330 of transfer unit 340 and by other the structure of auxiliary conveying liquid body medium, in the inside of housing 110, conventionally produce volume flow.This volume flow can be at least 5 times, at least 10 times, at least 15 times or at least 20 times of the liquid medium volume that provides of the inflow region 820 by clutch pack 100, but also can be less than above-mentioned numerical value.Here given ratio relates to by the maximum delivery of transfer unit 340.Conveyor surface 330 is just at corresponding fill fluid and form forced flow in the housing 110 of spin axis rotation, the positive good utilisation of this conveyor surface the driving side of clutch pack 100 and the effect of the different rotating speeds on slave end, i.e. different rotating speeds on driver part 150 and driven member 190.Conveyor surface 330 causes the circulation of liquid medium as the pump impeller in hydraulic coupling or torque converter or turbine.

Pump impeller hub 840 is connected with the first clamshell 120 of housing 110 by welding 870.The second clamshell 130 is also connected with anterior wheel hub 580 by welding 880, therefore, by for example may be embodied as weld seam and making that two clamshells 120,130 are interconnective is welded to connect the closed cavity volume that 140 formations have part cavity volume 730 and the first and second cavity volumes 720,740.

Corresponding welding 870,880 and 140 may be embodied as weld seam and soldering point at this.Certainly also can replace these interconnection techniques by being applicable to the interconnection technique of application conditions if desired.

Fig. 1 also shows weight balancing part 890, and this weight balancing part in the present invention with the first clamshell 120 welds mutually.This weight balancing part is uneven for collocation structure, assembly unbalanc or by the uneven of other conditional decisions and can reduce thus the corresponding degree of unbalancedness of power assembly system of vehicle.Yet as shown in Figure 1, in other embodiment, the position of weight balancing part can change.

Be configured to supply unit 810 and the housing 110 of a part for anterior wheel hub 580, saying between the second clamshell 130 space washer 900 is also housed exactly.As brief description, this space washer, for adjusting the gap between friction plate, is adjusted the gap between the first and second rubbing surfaces 230,240.Therefore, the gap between rubbing surface 230,240 determines ability and the reactivity when connection or cut-off clutch assembly 100 of the cut-out torque-flow of clutch pack 100 on the one hand.

When rubbing surface 230,240 needs reliable separation and needs greatly reliable separation torque-flow along with gap S change thus, must be by clamping element 620 this gap of cross-over connection in the situation that connecting and disconnect.Thus, just when being controlled ground engaging clutch assembly 100, can postponing and set up frictional connection, because before this must be by clamping element 620 overlap spans.Therefore, the adjustment in friction plate gap can improve the relation between reaction clutch ability and first and second wearing and tearing of rubbing surface 230,240 or the separating power of clutch pack 100 if desired.

For this reason, according to an embodiment's clutch pack 100, there is aforementioned space washer 900.What at this, can be in corresponding acceptable margin of error according to all parts size of all parts size of all parts size of inner attrition piece 270, outside friction disc 250, friction covering face 260 and other, may exist adjusts space washer 900 to the influential part dimension of friction plate gap S.At this, on the basis of the part dimension that friction plate gap can be measured above, realize, in the framework that also can install in (part) of clutch pack 100, realize and determine or measurement friction plate gap along spin axis 300 is corresponding.

If determine friction plate gap S with method in the above described manner, can for example use so a corresponding space washer 900 in a set of prefabricated space washer.Can certainly grind individually this space washer.After packing corresponding space washer 900 into, housing 110 that for example can closed clutch assembly 100 by the welding 870,880,140 shown in Fig. 1 after installation.

Space washer 900 can also be embodied as the embodiment of double-piece type or double-piece type.In the embodiment of space washer double-piece type or double-piece type, this space washer can comprise the first space washer parts and the second space washer parts, and these two space washer parts are along at least local profile with wedge shape of its circumference.Thus can be along spin axis 300 by the rotation relative to each other of two space washer parts, in axial direction by the rotation relative to each other of two parts, change the thickness of space washer.

Owing to packing the space washer of such double-piece type or multi-part type into, there is the space washer 900 of a plurality of space washer parts, as shown in Figure 1, can be by adjusting the friction plate gap S between rubbing surface 230,240 with respect to anterior wheel hub 580 rotation the second clamshells 130 in mounting point in the situation that at space washer 900.

In embodiment shown in Fig. 1, clutch pack 100, the second clamshell 130 has the planar section 910 on the outer surface of housing 110, for being fixed on this outer surface by clutch pack 100 or for welding screw housing 110 being fixed on the twisted plate of motor or other drive unit.For this reason, welding screw 160 is connected with the planar section 910 of housing 110 by welding 920.Yet housing 110 or the second clamshell 130 have recess 930 near on the internal surface 220 of inner volume in this region, the second clamshell 130 has than the strength of materials less in other regions in this region thus.The support 390 of outside friction disc 250 can be configured to thus, and this support extend in recess 930.This can make outside friction disc 250-1 be embodied as smooth disc, even if also do not need under difficult operating conditions to worry that section 370-1 or other drive faces 380-1 contact with housing 110.Can use thus the outside friction disc 250-1 identical with outside friction disc 250-2, and not need to consider to take special preventive measure in the region of section 370 or in other designed characteristic range.

The recess 930 that is arranged in planar section 910 opposites on housing 110 for example can form by the so-called S shape curved part in the region at the second clamshell 130.This S shape curved part can be along whole circumference setting at this, and planar section 910 can along circumferential restriction narrow and small, wherein can realize and the area of space being connected that welds screw 160.If S shape curved part is arranged on the second clamshell 130, thereby can provide this region by pushing S shape curved part in the region forming planar section 910 so.For example can remove and enter the material of internal surface 220 housing 110 inside, that enter the second clamshell 130 at this by turning or other milling process, to form recess 930.

For example, in clutch pack 100, in conjunction with Fig. 1, describe, for holding the manufacture method that clutch pack is fixed on to the planar section 910 of welding screw 160 on drive unit or other unit or other pins, can be important and necessary, in this clutch pack, need the specific position of power assembly system and part thereof.Therefore, the clutch pack shown in Fig. 1 100 be for example applicable to the structure of laterally assembling, transverse to the structure of the assembling of the vehicle longitudinal axis.Yet the embodiment of this clutch pack is far above and is limited to this clutch pack.This clutch pack also can be used in motor and the gearbox unit of longitudinal structure.

Only for the sake of completeness, should also be noted that clamping element 620 is not that connection by form fit connects with housing 110 here.If overcome the connection of the power transmission cooperation being caused by lug boss 690 and other parts and the connection of frictional fit, clamping element 620 can " freedom " rotation with respect to housing 110 so.For example can be at unexpected conversion rotating speed but this situation occurs while again not connecting clutch pack 100.Only bright for instance, vehicle starts braking until stop (driven member 190 stops) is exactly this situation from high engine speed.The rotating freely property of clamping element 620 may cause the region generating noise of clutch pack 100 under this situation, for example, can make driver feel to be interfered.

Fig. 2 shows the stereogram of transfer unit 340, such as being arranged in the framework of clutch pack 100 of Fig. 1.Transfer unit 340 is also referred to as friction plate drivening piece, and this transfer unit is embodied as whole ring substantially at this, is configured to annular.Transfer unit 340 has at this tooth 940 that a plurality of even circumferentials along transfer unit 340 arrange, and these teeth are in ring curved section 950 projections of transfer unit 340.Tooth 940 evenly arranges equidistantly at this.

Fig. 2 only represents each in a plurality of teeth with a reference character, at this each tooth, roughly has two flank of tooth that extend perpendicular to section 950, and these two flank of tooth form conveyor surface 330.For the tooth representing with tooth 940 in Fig. 2, two conveyor surface 330-1 and 330-2 interconnect by outer cover 960.

As described in describing about Fig. 1 above, in embodiment shown here, transfer unit 340 by riveting 350 and housing 110, be that the outer cover of clutch pack 100 is connected.In order to rivet, transfer unit 340 has corresponding hole 970 on some sections 950, by these holes, has realized the riveted joint with housing 110 or the second clamshell 130.More precisely, the transfer unit shown in Fig. 2 has six holes 970 altogether at this, and these holes are evenly distributed on the circumference of transfer unit 340.Certainly, also can implement the hole 970 of varying number in other embodiment, these holes can be evenly or the setting that also can distribute unevenly.

Transfer unit 340 is single type structure at this, by a definite monoblock blank, is made.Except blank raw material and hole 970 are provided, at this also by making the workpiece deformation of sheet manufacture transfer unit 340.Can adopt thus the relatively simply and therefore favourable manufacture method of cost.In other embodiment, also can adopt the manufacture method of cutting or foundry engieering to manufacture corresponding transfer unit 340, in these embodiments may be to the requirements at the higher level of load preferential or the requirements at the higher level of other boundary conditionss of other manufacture methodes are seemed to very important.

Fig. 3 shows perspective view or the stereogram of transfer unit arcuate section 980 equally.Transfer unit arcuate section 980 forms ring arc and the single type moulding by making the workpiece deformation of sheet equally at this.Transfer unit arcuate section 980 has and is about as much as 90 ° of arc length along circumference at this.If as shown in Figure 1, for example when jacket side is fixed, four corresponding transfer unit arcuate sections 980 engage successively, form transfer unit 340 as shown in Figure 1.In other words, according to embodiment transfer unit 340 in an embodiment of clutch pack 100, also can comprise a plurality of, four transfer unit arcuate sections 980 for example.Certainly, in other embodiment, also can use the transfer unit arcuate section 980 of other quantity, thereby according to providing transfer unit 340 in the framework of an embodiment's clutch pack 100.

Therefore, the transfer unit arcuate section shown in Fig. 3 comprises corresponding a plurality of tooth 940, and these teeth stretch out section 950 and on the side of tooth, have the conveyor surface 330 extending perpendicular to section 950 substantially.And conveyor surface 330 interconnects by outer cover 960.For fixing transfer unit arcuate section 980 on housing 110, this transfer unit arcuate section equally correspondingly have for the contact of riveting or peg graft, also may be for spinning or the hole of other technique for fixing.Yet, in the transfer unit arcuate section 980 shown in Fig. 3, be provided with two hole 970-1 and 970-2, the transfer unit 340 therefore mutually obtaining thus during series winding at four corresponding transfer unit arcuate sections 980 is by eight socket connections or riveting are connected with housing 110 altogether.

No matter the levels of precision implemented in the embodiment shown in fig. 1 of transfer unit 340 is how, according to a plurality of embodiments of an embodiment's clutch pack 100 can both be by the driving of first component 280, for example inner attrition piece 270 the common use by conveyor surface 330 realize form liquid medium, for example oil is mobile functional.Therefore, the embodiment of such clutch pack 100 can realize the drive of friction plate 270 in wet clutch, and does not need, for relevant inner attrition piece, extra friction disc support is set.Transfer unit 340 meets the additional function that blade is used to form inner oil circulation at the same time.According to an embodiment's clutch pack 100, at this, may be embodied as many friction disk clutchs or also may be embodied as single plate clutch.

In the many friction disk clutchs assembly shown in Fig. 1 by the element of bellows-shaped, be that transfer unit 340 has been realized the drive of friction plate 270 (first component 280).Transfer unit 340 can be embodied as shown in Figure 2 the design proposal of single type or be embodied as shown in Figure 3 a plurality of arcuate sections.Conveyor surface 330 produces inner oil circulation at this, but simultaneously for being with movable friction plate.

As shown in Figure 1, transfer unit 340 can start on pusher side to be connected to by riveted joint or other interconnection techniques on the outer cover of housing, on the second clamshell 130, so that the moment of torsion of motor is delivered on friction plate 270 at this.Embodiment shown in Fig. 1 to 3 represents that friction plate drivening piece is arranged on the clutch pack 100 of jacket side thus.To this, clutch pack 100 completely can be for the big or small moment of torsion of hundreds of Newton meter (Nm).But also can implement to transmit the higher or lower clutch pack of Maximum Torque 100 according to a plurality of embodiments.

Fig. 4 shows according to the corresponding whole system of an embodiment's clutch pack 100, but transfer unit 340 is fixed on piston side in this clutch pack.

Thus, as shown in Figure 4, although also have Sealing 360 according to an embodiment's clutch pack 100, no longer the riveting 350 by connection sealing element 360 and the second clamshell 130 (outer cover) is directly connected with transfer unit 340.The transfer unit 340 that for example Fig. 5 is shown specifically with 6 at this moment by riveting 990 with clamping element 620 form fit and can not be connected with the relative rotation.Transfer unit 340 for example can be connected with a plurality of leaf spring element 1010 form fit ground by other rivetings 1000 thus, and wherein leaf spring element 1010 is embodied as a part for Sealing 360.In this leaf spring element 1010 by using the forming materials of Sealing 360 and therefore making parts with the seal.But leaf spring element 1010 also can be used as independent part manufacture or by other manufacture method, manufacture leaf spring element with Sealing 360 single type moulding in the situation that in other embodiment.

Certainly, in other embodiment, also can implement other forms of moment of torsion transmission.For example can adopt for example not for holding the leaf spring element 1010 in the hole of riveting or other links.Moulding leaf spring element 1010 and it is also fine to internal strain in being greater than the scope of 120 ° for example crooked on the outer diameter of Sealing 360 or inner diameter first for example.Connection by frictional fit if desired realizes corresponding moment of torsion transmission and is also fine.

Because Sealing 360 by riveting 350 with outer cover, the second clamshell 130 can not be connected with the relative rotation, so realized substantially and can not counterrotatingly connect between the housing 110 as driver part 150 and clamping element 620.Therefore, Sealing 360 is here also as connected element 1015.Thus, with respect to the clutch pack 100 shown in Fig. 1, at this moment clamping element 620 no longer can " freedom " rotate, but is connected ordinatedly with housing 110 general shape.Therefore, even if flip-flop rotating speed and again do not connect clutch pack 100 also there will not be the corresponding situation about making a noise due to the clamping element 620 rotating freely in this embodiment.

Between clamping element 620 and housing 110 to be connected to this may be only substantially can not be counterrotating, this be because for example due to distortion, thermal effect or due to the feature of the geometrical shape by leaf spring element 1010 defineds clamping element 620 move axially process in can between clamping element 620 and housing 110, form and rotate.If but not affected by these factors, in embodiment shown here, clamping element 620 is followed rotatablely moving of housing 110.

In the change programme shown in Fig. 4, transfer unit 340 is arranged on piston side, wherein by leaf spring element 1010, is connected to the second clamshell 130 as outer cover, Engine torque is delivered on inner attrition piece 270 by conveyor surface 330.Leaf spring or leaf spring element 1010 have been set up transfer unit 340 thus to the connection of starting the second clamshell 130 of pusher side.Leaf spring element 1010 stretches in the first cavity volume 720 at this, so the mobile of formation fluid carried and helped thus to this cavity volume auxiliary fluid when housing 110 rotates and transfer unit 340 rotates with respect to the liquid medium in housing 110 inside thus.Leaf spring element 1010 contributes to oily conveying thus.

Even if roughly use riveting 990,1000,350 above, still also can adopt other interconnection technique for setting up and substantially can not counterrotatingly connect accordingly between housing 110 and transfer unit 340.Therefore, corresponding riveting can be individually or jointly by other interconnection techniques, for example socket connection, is replaced or supplement, but also can adopt the connection of other form fit, power transmission cooperation and/or material cooperation to replace or supplement.

In a corresponding embodiment, can replace leaf spring element 1010 by miscellaneous part, as long as these parts contribute to or at least can not stop clamping element 620 to move axially, move along spin axis 300.

Fig. 5 shows the schematic perspective view of the transfer unit 340 that can be used in embodiment shown in Fig. 4, clutch pack 100.This transfer unit 340 is structurally slightly different with the transfer unit shown in Fig. 2.Therefore this transfer unit 340 is also embodied as whole ring, and this ring is also to make by blank single type corresponding, sheet.Transfer unit 340 also has a plurality of teeth 940 here, and these teeth are in planar section 950 projections.Conveyor surface 330 is substantially perpendicular to these planar section 950 ground projections, outer cover 960 connections that these conveyor surfaces extend by being parallel to substantially section 950.Similarly, here some of them section 950 has hole 970, and transfer unit 340 can be connected with clamping element 620 by riveting by these holes.For fixing transfer unit 340, this transfer unit has six holes 970 in this case altogether, but can change the quantity in hole 970 in other embodiments.

In the transfer unit 340 shown in Fig. 5, in outer cover 960, do not illustrate for fixing hole or other structures of other rivetings 1000.But can in the some or all of outer cover 960 of tooth 940, corresponding hole be set from different shown in Fig. 5, transfer unit 340 can be connected with leaf spring element 1010 by these holes.Alternatively, also can, by leaf spring element 1010 is directly connected with hole 970 by riveting 990, save thus the enforcement of other rivetings 1000 if desired.Can avoid if desired thus tooth 940 to bear extra shear load.

Fig. 6 shows schematic diagram corresponding with Fig. 3, transfer unit arcuate section 980, and this transfer unit arcuate section is embodied as equally the parts of ring arc and forms substantially 90 ° of arcuate sections of transfer unit 340.Yet relate to again the transfer unit arcuate section 980 for being fixed in piston side of transfer unit 340 here.As shown in Figure 6, transfer unit arcuate section 980 can have according to the embodiment of corresponding transfer unit 340 other the unshowned hole of Fig. 6 in the region of outer cover 960.In addition, aspect size, this transfer unit arcuate section is substantially corresponding to the transfer unit arcuate section 980 shown in Fig. 3, and this transfer unit arcuate section is provided for fixing in piston side as shown in Figure 5.The orientation of tooth 940 and conveyor surface 330 is also interpreted as corresponding.

Fig. 7 shows according to another embodiment of an embodiment's clutch pack 100.On some parts that clutch pack shown in clutch pack 100 shown in Fig. 7 and Fig. 4 is described below, there is difference.But these two clutch packs 100 are only having small difference aspect other parts.

First can see, as shown in Figure 7, clutch pack 100 has inner attrition piece and the outside friction disc 270,250 of lesser amt.More precisely, clutch pack 100 only has respectively an outside friction disc 250 and an inner attrition piece 270.The inner attrition piece 270 that represents first component 280 is meshed by the drive face 320 of section 310 and the conveyor surface 330 of transfer unit 340 again at this.Correspondingly, transfer unit 340 is shorter along spin axis 300, i.e. stretching, extension in axial direction.

In addition, the difference of the clutch pack shown in clutch pack 100 and Fig. 4 is also, can axial lead driven member 190, be that two bearings 565,550 of bottom wheel hub 200 are embodied as axial needle bearing in this clutch pack 100.Certainly, in other embodiment, also can adopt other rolling bearing axially and/or radially or sliding bearing and mixed form.

The difference of the clutch pack shown in the clutch pack 100 shown in Fig. 7 and Fig. 4 is also, the second clamshell 130 neutralizes the first clamshell 120 overlaids in the region that is welded to connect 140, outwards limit clutch pack 100 and housing 110 thereof.Correspondingly, the position of weight balancing part 890 is no longer arranged on radially outer, but is arranged in the side away from welding screw 160 of housing 110.

In addition, the difference of the clutch pack shown in the clutch pack 100 shown in Fig. 7 and Fig. 4 is, is provided with cup spring 1020 and replaces Sealing 360 between the second clamshell 130 and clamping element 620.Cup spring 1020, at this Sealing 360 as shown in Figure 4 pretension that is equally under pressure, is therefore again normally disengaged clutch assembly according to an embodiment's clutch pack 100.Different from Sealing 360, cup spring 1020 must not be the element that can seal, and the first and second cavity volumes 720,740 shown in Fig. 4 can form common cavity volume 1030 here thus.The elastic element that certainly, also can adopt other in other embodiment is as cup spring 1020.Therefore,, according to structure, common cavity volume 1030 can be divided into again corresponding the first and second cavity volumes 720,740.

Cup spring 1020 can be replaced with for example diaphragm spring, helical spring structure or other elastic elements equally.Certainly, in other embodiment, can also make the elastic element under tension pretension of cup spring 1020 or replacement cup spring 1020.Correspondingly, according to an embodiment's clutch pack 100, are normal-close clutch device assemblies.

Connected element 1015 is for being established to substantially can not counterrotatingly connecting of transfer unit 340 in the present embodiment, and this connected element is by riveting 350 and outer cover, i.e. the second clamshell 130 mechanical connection with the relative rotation.But also can on this position, use other interconnection technique in other embodiment.

Connected element 1015 has a plurality of leaf springs 1010, and these leaf springs are to be formed into substantially can not being counterrotatingly connected of transfer unit 340 according to the mode described in Fig. 4 and method.For this reason, connected element 1015 and leaf spring 1010 thereof are by other riveting 1000 and transfer unit 340 mechanical connection with the relative rotation.But here can also adopt other for example according to the interconnection technique described in Fig. 4.

But clamping element 620 is constructed different in the clutch pack 100 shown in Fig. 7.Although clamping element 620 still has piston 610, also comprise extraly the cup spring 1040 that reclines.This cup spring 1040 that reclines is configured to the structure of general toroidal at this.This cup spring that reclines contacts with inner attrition piece 270 on the region of the radial outer end near the cup spring 1040 that reclines, this inner attrition piece 270 also represents first component 280 here, and the cup spring that reclines is supported on the convex shoulder 1050 of clamping element 620 with the region that is positioned at inner radial of the cup spring 1040 that reclines.Obtain thus in Fig. 7 unshowned in the region of convex shoulder 1050, the cup spring 1040 that reclines on the region in inner radial is with respect to the spacing between inner attrition piece 270 or gap S2.

The convex shoulder 1050 of clamping element 620 only extends at this on little radial zone, and radially outward has a flanged structure 1060 with compression point 1070 to be connected on this region.Compress the point of the point 1070 the most approaching cup springs 1040 that recline at this ordinary representation flanged structure 1060.In the home position of clamping element 620, compress point 1070 at this in axial direction, along spin axis 300, have distance recline spacing or the gap S2 of cup spring 1040, this gap can not surpass gap S1.This external compression point 1070 has the vertical interval apart from spin axis 300, and this spacing is greater than convex shoulder 1050 stretching, extension radially, but there is no to surpass the outer diameter of the cup spring 1040 that reclines.

In other words, because gap S2 surpasses gap S1, be even less than if desired this gap, so clamping element 620 puts 1070 by compression, at the At The Height of friction radius, abut in and recline on cup spring 1040 substantially.Size by corresponding flange radius can limit or definite compacted position.More precisely, so to compress point 1070 may be more compression line because clamping element 620 and the cup spring 1040 that reclines are the structure of turn round shape substantially.

If at this moment operate clamping element 620, make this clamping element towards the direction motion of rubbing surface 230,240, the cup spring 1040 that reclines so produces or reinforcement is applied to the power on inner attrition piece 270.To this, because this cup spring that reclines of structure of the cup spring 1040 that reclines can deform, the cup spring that makes thus to recline is out of shape and on inner attrition piece 270 " expansion " slightly.May make thus the spacing of maximum power effect move on to like a cork on inner attrition piece 270.Due to the point that is configured in this maximum impacting force of friction packs 180 just almost and in the region of friction covering face 260, occur that the radius of maximum impacting force is consistent.Therefore this radius is also referred to as friction radius.

If at this moment clamping element 620 continues motion, make to compress point 1070 and form and contact with the cup spring 1040 that reclines when overlap span S2, compress so point and apart from the radial spacing of spin axis 300, limit the position of friction radius.Can limit more targetedly friction radius thus, this can make wearing and tearing, inhomogeneous loss still less and/or the heat radiation of the liquid medium of the rubbing surface 230,240 of flowing through better.With respect to shown in Fig. 1 and Fig. 4, being configured in this and only having increased on a small quantity extra number of components of clamping element 620 because at this moment implemented extraly the cup spring 1040 that reclines.

Certainly, in other embodiment, also can implement and there is the different geometrical shape of flanged structure that compresses point 1070.The seal face with more than one compression point 1070 for example also can be set and substitute single compression point 1070.Equally can be with diaphragm spring or the another kind of elastic element cup spring 1040 that replaces reclining.

The transmission input shaft 1080 that Fig. 7 also schematically shows is foregoing, have the outer toothed portion 1090 being engaged in internal tooth portion 210, it has been realized bottom wheel hub 200, has been can not counterrotatingly connecting of driven member 190.As mentioned above, outer toothed portion 1090 lacks several teeth, can make liquid medium flow to inflow region 820.

In addition, Fig. 7 shows the groove with Sealing 1100, and this groove is along circumferentially extending between inflow region 820 and the input hole 650 in piston pressure chamber 590 around transmission input shaft 1080.This groove and anterior wheel hub 580 contact and seal inflow regions 820 with respect to input hole 650.In order to be input hole 650 and piston pressure chamber 590 supply liquid mediums, transmission input shaft 1080 also has flow channel 1110, and this flow channel is symmetrical arranged along spin axis 300.By attachment hole 1120, can be used for filling piston pressure chamber 590 for flow channel 1110 supply liquid mediums.

Fig. 8 shows according to another embodiment of the clutch pack 100 described in an embodiment, wherein except the space washer 900 having illustrated, is also integrated with another space washer 900 ' above.As previously mentioned, another space washer 900 ' may be embodied as the space washer of single type or multi-part type equally at this.Space washer 900 ' is arranged between dividing plate 570 and clamping element 620 in 590 regions, piston pressure chamber at this.Also can change friction plate gap S by changing the position of clamping element 620 thus.Together with space washer 900, by changing the spacing of the second clamshell 130 or can changing friction plate gap S by changing the spacing of clamping element 620.

Certainly implement two space washers 900,900 ' definitely optional simultaneously.During in implementing two space washers 900 one, just can correspondingly adjust friction plate gap S, and not increase whereby the required structure space of clutch pack 100.No matter be, use single space washer 900 or 900 ' still use two space washers 900,900 ' can both adjust friction plate gap S and can reduce axial arrangement space required, clutch pack 100 with respect to traditional technological scheme simultaneously.

In addition, embodiment shown in Fig. 8, clutch pack 100 and the clutch pack shown in Fig. 7 are as broad as long, so here with reference to the description of figure 7.

Last Fig. 9 shows another change programme of the clutch pack 100 shown in Fig. 7, and the basic distinction of this clutch pack and clutch pack 100 is, does not implement recess 930.Therefore support 390 is constructed shortlyer in the axial direction, the section 370 that makes thus to have another drive face 380 of outside friction disc 250 bends to hook-type, this outside friction disc also represents second component 290, crooked to the direction away from the second clamshell 130 with the angle of predetermining with respect to spin axis 300.

Except this changes, the clutch pack 100 shown in the same and Fig. 7 of the clutch pack 100 shown in Fig. 9 does not have difference.

The embodiment of clutch pack 100 can also be with movable friction plate when can provide wheel blade function at the liquid medium in can the housing 110 in clutch pack 100.These clutch packs 100 can be for different clutch application, for example, for having the vehicle of the automatic transmission that is arranged on front part of vehicle region and constructs transverse to direction of travel.According to an embodiment's clutch pack 100, can be used as starting clutch, but also can be for combining synchrom esh transmission or longitudinal cut-off clutch that has assembled motor.As liquid medium, for example can use oil.

Above-described embodiment is only principle explanation of the present invention at this.Structure described here and the modification of detail and change programme are for other professional workforces can be understood.So be only intended to by the protection domain of following claim and be not by for example limiting the present invention according to the detail of embodiment's described here description and explanation.

Claims (15)

1. clutch pack (100), described clutch pack is for example for vehicle engine assembly system, and described clutch pack has following feature:

At least local first component (280) that is disc-shaped, described first component has the first rubbing surface (230) on the section of disc-shaped;

At least local second component (290) that is disc-shaped, described second component has the second rubbing surface (240) on the section of disc-shaped, and wherein said the first rubbing surface (230) and the second rubbing surface (240) are constructed and are provided for mutually to form friction engagement and contact with liquid medium in the running; And

Transfer unit (340), described transfer unit comprises the conveyor surface (330) for liquid medium, and described transfer unit and driver part (150) can not connect substantially with the relative rotation, make described conveyor surface (330) when rotating with respect to liquid medium, realize flowing of liquid medium; And

Wherein, described transfer unit (340) is by the engagement of conveyor surface (330) and described first component (280), make when transfer unit (340) rotates described in first component (280) be rotated.

2. according to clutch pack claimed in claim 1 (100), wherein, described first component (280) is by drive face (320) and transfer unit (340) engagement, and making the surface of contact maximum between described drive face (320) and described conveyor surface (330) is 50% of described conveyor surface (330) area.

3. according to clutch pack in any one of the preceding claims wherein (100), wherein, described conveyor surface (330) is continuous and smooth.

4. according to clutch pack in any one of the preceding claims wherein (100), wherein, described conveyor surface (330) is approximately perpendicular to tangent direction orientation, and described tangent direction is perpendicular to the spin axis (300) of described first component (280) and perpendicular to vertically away from the radial direction of described spin axis (300).

5. according to clutch pack in any one of the preceding claims wherein (100), wherein, described transfer unit (340) is roughly annular.

6. according to clutch pack claimed in claim 5 (100), wherein, described transfer unit (340) single type ground structure or described transfer unit (340) comprise the transfer unit arcuate section (980) of a plurality of ring arcs, wherein transfer unit arcuate section (980) the single type ground structure of each ring arc.

7. according to clutch pack claimed in claim 6 (100), wherein, the distortion of the transfer unit arcuate section (980) of described transfer unit (340) or ring arc by sheet-like workpiece, by the manufacture method of cutting or foundry engieering, manufacture.

8. according to clutch pack in any one of the preceding claims wherein (100), wherein, described driver part (150) be can be enough the liquid medium housing (110) of filling or having filled, and described transfer unit (340) is connected with described housing (110) by the connection of form fit substantially.

9. according to clutch pack claimed in claim 8 (100), wherein, described transfer unit (340) can not be connected with described housing (110) with the relative rotation by riveting (350) and/or socket connection.

10. according to clutch pack claimed in claim 8 (100), described clutch pack also has clamping element (620), described clamping element constructs and is provided for made the first rubbing surface (230) and the second rubbing surface (240) mutually form friction engagement and/or departed from friction engagement by operation, wherein, described transfer unit (340) for example can not be connected with described clamping element (620) with the relative rotation by riveting (990) and/or socket connection, wherein, described housing (110) for example can not be connected with connected element (1015) with the relative rotation by riveting (350) and/or socket connection, and wherein, described connected element (1015) for example can not be connected with described transfer unit (340) substantially with the relative rotation by riveting (1000) and/or socket connection.

11. according to clutch pack claimed in claim 10 (100), wherein, described connected element (1015) has a plurality of leaf spring element (1010), described leaf spring element is for example connected by riveting (1000) and/or socket connection form fit ground with described transfer unit (340), to form and substantially can not counterrotatingly to connect between described transfer unit (340) and described connected element (1015).

12. according to the clutch pack described in any one in claim 8 to 11 (100), wherein, described first component (280) comprises the disc-shaped parts with central recess, wherein said the first rubbing surface (230) is arranged on the directed main surface of the spin axis (300) of the described first component of being approximately perpendicular to of disc-shaped parts (280), wherein on a side stretching into the section (310) in central recess of disc-shaped parts, realize the engagement with described transfer unit (340), wherein said second component (290) comprises another disc-shaped parts with central recess, wherein said another disc-shaped parts are meshed with support (390) in its outer radius.

13. according to the clutch pack described in claim 12 (100), described clutch pack also has clamping element (620), described clamping element constructs and is provided for made the first rubbing surface (230) and the second rubbing surface (240) mutually form friction engagement and/or departed from friction engagement by operation, wherein, described clamping element (620) limits first cavity volume (720) of filling with liquid medium at least partly, the cross-section area maximum having in the transversal plane that described the first cavity volume extends therein at spin axis (300) is equivalent to 20 times of the cross-section area of described conveyor surface (330) in described transversal plane.

14. according to the clutch pack described in claim 13 (100), wherein, described clamping element (620) has the port hole (305) that enters described the first cavity volume (720) for liquid medium, described port hole is disposed radially near the At The Height of described conveyor surface (330) or described spin axis (300), can flow through first component (280) and/or second component (290) and support (390) of liquid medium under the operating condition in friction engagement wherein, make by conveyor surface (330), to cause that liquid medium radially outward is by the first rubbing surface (230) and/or the second rubbing surface (240) or flowing along the first rubbing surface and/or the second rubbing surface when conveyor surface (330) rotates with respect to liquid medium.

15. according to clutch pack in any one of the preceding claims wherein (100), described clutch pack also has clamping element (620), described clamping element constructs and is provided for made the first rubbing surface (230) and the second rubbing surface (240) mutually form friction engagement and/or departed from friction engagement by operation, wherein, described clamping element (620) has the port hole (305) that enters the first cavity volume (720) for liquid medium, described port hole be radially arranged on the At The Height of described conveyor surface (330) or spin axis (300) near, can flow through first component (280) and/or second component (290) and support (390) of liquid medium under the operating condition in friction engagement wherein, make by described conveyor surface (330), cause liquid medium radially outward by the first rubbing surface (230) and/or the second rubbing surface (240) or flow along the first rubbing surface and/or the second rubbing surface when described conveyor surface (330) rotates with respect to liquid medium.